Gear transmission



W. K. MCIVER GEAR TRANSMISSIQN Filed May 24, 1947 May 16, 1950 inventor: A William KnMcIverx His Attorney 4 l I f,

Patented May 16, 1950 2,508,121 GEAR TRANSMISSION William K. McIve-r, Fort Wayne, Ind., assigner to General Electric Company, a

New York corporation of Application May 24, 1947, Serial No. 758,184

(Cl. 'i4-804) 3 Claims. 1

This invention relates to speed changing gear transmissions and more particularly to such transmissions utilizing an eccentrically driven gear which meshes with an internal gear.

An object of this invention is the provision of 'an improved speed changing gear transmission.

Another object of this invention is the provision of an improved speed changing gear transmissionwherein vibration is substantially eliminated.

ther objects and advantages of this invention ll become apparent and this invention will be better understood from the following description referring to the accompanying drawing, and the features of novelty which characterize this invention will be pointed out with particularity in the claims annexed to and forming a part of this specification.

A feature of this invention is the provision of a plurality of eccentrically driven pinions which mesh with an internal gear having a greater number of teeth. Motion is transmitted from the pinions to the driven shaft by a multiple pin and aperture connection. By utilization of the proper number of such pins, pulsations producing undesirable vibration are effectively eliminated. ifi-entrifugal forces due to the eccentric throw of the pinions and the tendency of the pinions to form a couple have been cancelled by proper proportionment and positioning of the pinion gears.

In the drawing, Fig. 1 is a side elevational view, partly in section, of an embodiment of this improved gear transmission. Fig. 2 is a cross section view taken along line 2-2 of Fig. 1. Fig. 3 is a side Yelevational view, partly in section, of another embodiment of this invention and Fig. 4 is a cross section taken along the line 4--4 of F18. 3.

Referring now to Fig. l, there is shown an embodiment of this invention having driving shaft I, driven shaft 2, and enclosing case 3 having end plate l secured by any suitable means such as bolts 8. 'I'he shafts I and 2 are suitably journaled in bearings 22 and 23. Driving shaft I is Wovided with three eccentrics i, 1, and 8. These eecentrics are true circles in form, and the axis of eccentricity of the outer eccentrics 6 and 8 are identically oriented. The axis of eccentricity of intermediate eccentric 'I is disposed 180 to the outer eccentrics i and 8. Conoentrically arranged and freely rotating on eccentrics 6, l, and 8, are pinion gears S, I8, and I I. Stationary case 3 is provided with an internal toothed surface with which a number of the pinion teeth mesh. As shown in Fig. l, due to the relative position of the eocentrics. pinions 8 and II will be meshing with gear I2 at the same point while pinion 'Il will 2 be meshing with gear I2 at a point 180 disposed from the points of contact of the outer two pinions. Internal gear I2 is provided with a greater number of teeth than the mating pinions 9, It, and II. In a machine of this type which I have constructed, the internal gear was provided with etteth while the pinions were provided with 64 It will now be apparent, that as driving shaft I is rotated causing eccentrics 6, I and 8 to rotate, pinions 9, I8, and II will be given a rolling motion around gear I2. If the gear I2 and pinions 6, 'I and 8 were provided with the same number of teeth. rotation oi. the driving shaft I would not cause the pinions to rotate since the pinion teeth in their rolling action would always mesh with the same teeth on the internal gear. However, assuming that gear I2 has one more tooth than the pinions, one revolution of driving shaft I causing the pinions to roll around gear I2 will cause the pinions to rotate the distance of one tooth in the opposite direction from the direction of rotation of driving shaft I, as shown by the arrows I3 and Il in Fig. 2. This is due to the fact that the 64 tooth pinions in rolling around the 65 tooth internal gear in one revolution of driving shaft I mesh with 64 teeth of the gear. Thus, when the driving shaft has completed one revolution, the pinions are one tooth away from their starting point, and, as shown in Fig. 2, pinion tooth I5 which was initially meshed with gear tooth i6, after one revolution, is now meshed with gear tooth I1.

It can now be seen, that for each revolution of driving Shaft I in direction i3, the pinions will advance one tooth in direction I4. Therefore, in a machine having a 65 tooth gear and pinions with 64 teeth, the pinions will complete one full revolution for each 64 shaft revolutions, or a 64/1 speed reduction ratio. As can be seen, the rotation of the pinions is superimposed on the rolling eccentric motion around internal gear I2.

While pinions 9, I0, and II are completing one revolution for each 64 revolutions of driving shaft I, some means must be provided to transmit this motion to driven shaft 2. In order to accomplish this motion transfer, the arrangement now to be described is provided. Driven shaft 2 is provided with a spider member I 8 having a plurality of pins I9. For reasons to be hereinafter explained, these pins should be an odd number over seven, nine being shown here. These pins are parallel to the driven shaft 2, equidistant from its axis, and spaced equally annularly. The driven shaft 2 and spider member I8 are concentric with driving shaft I and projection 2li of the driving shaft may be suitably iournaled in recess 2| in the spider member for supporting purposes.

Pins I9 are rigidly secured to spider member I0 and extend axially substantially beyond the first pinion 9. Each pin is provided with a freely rotating bushing 2l. Pinions l, I0, and Il, are provided with circular apertures 25 equal in number to pins I9 and. similarly spaced, the centerline of the apertures 2l defining a circle equal in radius to the circle of centers of the pins I 9. Pins Il and bushings 24 extend through the apertures 2l and are seated therein as shown in ngt will now be readily seen that rotation of the pinions caused by rotation of the driving shaft I will be transmitted to the spider member Il and to driven shaft I. have an eccentric rolling motion, it is essential that the diameters of apertures 25'be properly proportioned so that bushings 24 will roll around the inner peripheries of the apertures with no sliding motion. It has been found that an aperture diameter equal to the sum of the bushing diameter and the amount of eccentric throw of the eccentrics is the proper diameter to secure this rolling action. The eccentric throw of an eccentric is equal to twice the eccentricity, the eccentricity being the distance representing the displacement of the center of the eccentric and the center of rotation.

An inspection ofFlg. 2 will indicate that as the pinion rotates in the direction of the arrow I I, pressure will be applied by the walls of apertures 25 to drive pins I0 in the same direction. This pressure is applied in pulsations successively to each pin as the pinion rolls eccentrically around the gear I2. Thus, for each revolution of driving shaft I, there will be nine driving pulsations applied by the nine apertures 25 on the nine pins I3. If a single driving pinion were utilized and the driving shaft I was rotating at 1000 R. P. M., this would result in a vibration frequency of 9000 pulses per minute. If an even number of pins and apertures is utilized, for instance 8, provision of two or more pinions, aS shown here, would not change the pulsation frequency since opposite pins would receive maximum thrusts simultaneously from the two pinions. However, if an odd number ofpins are used, as shown here, with two or more pinions, adjacent pinions being disposed 180 to each other, instead of 9 pulsations or thrusts per revolution of the driving shaft I, there are 18 per revolution, the thrusts being staggered since no two pins are in direct opposition. It has been found that 9 pins is the minimum number which will effectively reduce the vibration due to the driving pulses. With nine pins, a driving speed of 1000 R. P. M. results in a pulsation frequency of 18,000 per minute. It was found that machines provided with an even number of pins were subject to excessive resonant vibrations when operated at high speeds on the order of 10,000 to 15,000 R. P. M. However, with the provision of 9 pins, the resonant frequency is thrown beyond the operating range of the machine and the magnitude of the pulses is reduced.

The vibration due to the thrusts or pulsations driving the pins Il is not the only source of vibration in such a device. Another source of vibration is due to the centrifugal forces produced by the eccentric throw of the eccentrics. To effectively balance out these centrifugal forces, two pinions can be provided with their eccentrics disposed to each other by 180. How- Since the pinions ever, at high speeds, it has been found that a couple develops between the two pinions. Therefore, the arrangement shown in Pig. I using three pinions is provided. Here, the intermediate ptnion i0 is disposed 180 from the two outer pinions 9 and il, is proportioned so that its weight equals the combined weights of the outer two pinions, its thickness being twice that of one of the outer pinions. This arrangement effectively cancels the couple effect normally produced by two eccentrics rotating at high speed.4 In effect, this arrangement provides two pinions disposed apart for canceling the centrifugal forc due to eccentric rotation. however, one of the pinions is split and the two halves placed on either side of the central pinion in order to can cel the couple ei'fect present with two eccentrl.

Referring to Fig. 2, it will be seen that the teeth of pinions I, Il, Il, and gear I2, are somewhat shorter than normal. It was found that the most emcient operation was secured using standard involute teeth, however, with the tops cut off. Due to the fact that the gearing is internal, there is a necessary limitation to a short addendum and therefor to only about six tenths of a tooth in the arc of action. In one machine constructed having 65 gear teeth and 64 pinion teeth, with the eccentricity of the eccentrics .0208", the pitch diameter of the pionion was 2.667", the pitch diameter of the gear 2.7083". the gear addendum .017", the pinion addendum ,.017", and the clearance between the gear teeth and pinion teeth .0076".

As seen above, the device described in Pigs. l and 2 furnishes a 64/1 ratio with 65 gear teeth and 64 pinion teeth, the direction of rotation of the driven shaft 2 being opposite from the direction of rotation of the driving shaft I.

In order to secure operation of the driven shaft in the same direction as the driving shaft, the arrangement now to be described is provided. Referring now to Figs. 3 and 4, there is shown another embodiment of this invention in which the pins are held stationary and the rotation transmitted to the internal gear. Here, the device is provided with driving shaft 2l and driven shaft 2l respectively Journaled in anti-friction bearings 22 and 2! in stationary enclosure 3l and 3|. Driving shaft 26 is provided with eccentrics 32 and 33 on which are mounted antifriction bearings 34 and 33. Pinion gears 30 and 31 are respectively mounted on bearings 34 and 35 and, due to the positioning of eccentrics 32 and 33 with 180 displacement, are oppositely displaced with respect to the center line of the shaft 26. Driven shaft 2l is provided with internal gear 3l having internal teeth 3l. Gear 3l may be supported on enclosure 3| with bearings Il and driving shaft 26 may be supported in enclosure 30 by bearing 4I.

As shown in Fig. 4, a plurality of teeth of the pinions 36 and 31 mesh with the teeth 33 of internal gear 33. Enclosure 3l is provided with a plurality of pins I2. As described above, the number of pins should be an odd number at least nine. These pins are provided with rotatable bushings 43 and are respectively seated in corresponding apertures 44 and 45 in pinions 33 and 31. These pinions and apertures are proportioned and arranged in the manner described under the discussion of Pigs. 1 and 2 above.

In operation, rotation of driving shaft 23 and eccentrics 32 and 33 causes pinions 30 and 3l to roll eccentrically about gear 33. However, since pins I2 are restrained, the eccentric motion will s be the only motion imparted to the pinions. As the pinions eccentrically roll, apertures Il will be in constant rolling contact with bushings Il. It will now be readily apparent that due to the difference in teeth, again assuming the gear to have 65 teeth and pinions 64 teeth, when the pinions have completed one eccentric roll and returned to their initial position, pinion tooth 46 which initially meshed with gear tooth 41 will now mesh with gear tooth Il, thus advancing the internal gear one tooth for each revolution of the driving shaft 26 in the same direction as the arrangement provides a reduction of 65/1 and the rotation of driven shaft 21 will be in the same direction as driving shaft 26.

While the three-pinion arrangement shown in Figs. 1 and 2 is not shown in Figs. 3 and 4, it is to be understood that it could be utilized instead of the two-pinion arrangement shown if the speeds to be used are such that the presence of the couple becomes objectionable. In this embodiment, provision is made against thrust and pulsation vibration by the utilization of nine or more odd pins and the vibration due to centrifugal forces from the eccentric throw is canceled by provision of two pinions 180 disposed to each other. Tooth design in Figs. 3 and 4 would be similar to that described in Figs. 1 and 2.

It can be readily understood that this arrangement will provide a compact and efiicient speed reduction unit with a minimum of vibration. A machine has been operated from 1000 to 12,000 R. P. M. with loadings from 120 lb. inches to 600 lb. inches with an average efciency of 81%. It was found that there was no change of emciency with the same load over the entire speed range. At 200 lb. linches, the eiliciency remained 83.2% from 1000 to 8000 R. P. M. That the device is capable of operation at exceptionally high speeds is indicated by that fact that a machine using it has been operated up to 20,000 R. P. M.

While I have shown and described particular embodiments of this invention, modifications thereof will occur to Vthose skilled in the art. I desire it to be understood therefore, that this invention is not to be limited to the particular arrangements disclosed and I intend in the appended claims to cover all modifications which do not depart from the spirit and scope of this invention.

What I claim as new and desire to secure Letters Patent of the United States is:

1. A speed changing device comprising, a driving shaft having three eccentrics thereon, the eccentric intermediate the outer eccentrics being disposed 180 therefrom, three pinion gears respectively arranged concentric with and freely rotating on said eccentrics, the pinion intermediate the outer pinions being equal in weight to the combined weights of the two outer pinions, a stationary internal gear having a greater number of teeth than said pinions, each of said pinions having a plurality of teeth in mesh with said internal gear and being adapted to roll thereon in response to rotation of said eccentrics, a driven shaft, a member secured to said driven shaft and having a plurality of rotatable parts projecting therefrom, said parts being parallel to the axis of said driven shaft and equi-distant therefrom and equally spaced annularly, said pinions having a corresponding number of circular apertures therein similarly spaced, each of said rotatable parts extending through and seated in the corresponding apertures in said pinions shaft rotation. It can now be seen, that this whereby said parts roll around the inner periph-` ery of said apertures as said pinions are rolled around said internal gear.

2. A speed changing device comprising, a driving shaft having three eccentrics thereon, the eccentric intermediate the outer eccentrics being disposed 180 therefrom, three pinion gears respectively arranged concentric with and freely rotating on said eccentrics, the pinion intermediate the outer pinions being equal in weight to the combined weights of the two outer pinions, a stationary internal gear having a greater number of teeth than said pinions, each of said pinions having a plurality of teeth in mesh with said internal gear and being adapted to roll thereon in response to rotation of said eccentrics, a driven shaft, a member secured to said driven shaft and having an odd number of pins over seven, said pins being parallel to the axis of said driven shaft and equi-distant therefrom and equally spaced annularly, said pinions having a corresponding number of circular apertures therein similarly spaced, each of said pins having a bushing and extending through and seated in the corresponding apertures in said pinions whereby said bushings roll around the inner periphery of said aper- Y tures as said pinions are rolled around said internal gear, the diameter of said apertures being equal to the diameter of said bushings plus twice the eccentricity of said eccentrics.

3. A speed changing device comprising, a driving shaft having three eccentrics thereon, the eccentric intermediate the outer eccentrics being disposed therefrom, three pinion gears respectively arranged concentric with and freely rotating on said eccentrics, the pinion intermediate the outer pinions being equal in weight to the combined weights of the two outer pinions, a stationary internal gear having a greater number of teeth than said pinions, each of said pinions having a plurality of teeth in mesh with said interna] gear and being adapted to roll thereon in response to rotation of said eccentrics, the teeth of said internal gear'and said pinions being of involute form with the tops removed providing a shortened addendum substantially 1%, of a normal v tooth, a driven shaft, a member secured to said REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 1,194,904 Wagner Aug. 15, 1916 1,647,191 Norton Nov. 1, 1927 1,770,035 Heap et al. July 8, 1930 1,833,648 Johnson Nov. 24, 1931 FOREIGN PATENTS Number Country Date 23,128 Switzerland i Apr. 8, 1901 79,704 Switzerland Jan. 2, 1919 

